DE19614226A1 - Unused mechanical energy recovery device for continuously variable transmission (CVT) and motor automatic transmission - Google Patents

Abstract

The device allows recovery on non-utilised mechanical energy in the pressurised oil system of the continuously variable transmission (CVT), using a valve (16) at the discharge outlet of the pressure, lubrication, or cooling oil circuit (14), directing a tangential oil jet onto a rotary or translatory part (5) of the transmission. The jet provides a force or torque pulse for the transmission component, allowing part of the hydraulic energy to be converted back into mechanical energy for the drive transmission path.

Description

The invention relates to a device for saving energy by recovery mecha African, unused energy from pressure and lubricating oil circuits from CVT's and Automobile gear shift automatic.

CVT's are part of the state of the art, economically favorable, and pleasant driving experience future-oriented vehicle drive concepts. More about their execution, Function and application criteria are contained in references / 1 / to / 5 /. Such gears require Pressure medium supplies to ensure the contact pressure of the friction drive, the provision pressure medium flows for the transmission adjustment processes, as well as lubricating and Coolant supply facilities. The specific supply needs for ensuring a safe Friction - especially with spontaneous torque peaks - and for the introduction of over settlement adjustment activities are relatively high and vary greatly depending on the operating state; about this also referred to / 61 and / 71. With constant supply of sufficient pressure medium for opening Bring the pressure of the friction drive and its translation adjustment occur relatively high pump drive losses. This is particularly because the pump dimensioning on the lowest operating speeds, where there is still the highest adjustment volume requirement, must be coordinated. Thus, in frequently occurring part-load operating states Automotive use this loss share relatively large.

Such transmission systems also have a relatively large need for lubricating and cooling oil, particularly on the friction parts of the friction drive to dissipate the inevitable heat. The obvious use of economical, controllable pumps for the separate supply of the pressure and Verstelldruckölkreises on the other hand is a structurally complex and therefore unfavorable Druckmit compared to the supply concept, since then another lubrication and cooling oil supply facility is required.

Conventional or well-known test and pre-series - CVT concepts have only one Constant hydraulic pump for both hydraulic circuits with different pressure levels, with the excess, or the unused pressure medium of the high pressure circuit then lubrication and cooling systems is fed. Such solutions, which are unfavorable in terms of pump drive losses, contain solutions but again the advantage that they are sufficient for the pressure and for the adjustment processes Keep the required print quantities available - especially for spontaneous needs - with a relatively small amount constructive effort. This means that for most operating times, no adjustment work is required However, a relatively high pump drive power is required, which is reflected in the energy balance Loss.

From the patent literature z. B. / 8 / to / 11 / are already various measures to reduce the Pump losses, especially for CVT's, are known, such were also in CVT test projects  Facilities already successfully used. However, such facilities require a certain amount additional, compared to the present solution, greater construction costs. They can also be relatively sluggish dynamic functional behavior may be disadvantageous for modern CVT concepts; on related dynamic requirements are dealt with in Ref. / 12 /.

A CVT adjustment strategy according to / 13 / is known to reduce the pump losses, in particular, which causes the constant provision of adjustment volumes that are required sporadically, the principle of which the exemplary embodiment according to FIG. 11 is based on. Here, however, the obligatory extensive lubricant and coolant supply requirement is not taken into account, which is relatively large in terms of quantity (approx. 1.5 l per lkW power loss). If this supply requirement is taken from a bias circuit with pump 90, which is designed to be large enough for this purpose, high losses again occur. Additional low-pressure supplies for cooling purposes require increased construction costs. The present inventive concept is therefore also matched to such a CVT control system.

In addition to the above-mentioned easily recognizable pressure oil supply relating to the functions There are still quasi-hidden needs that can be used to compensate for elastic deformations result under shock loads (required refilling and pressure increase requirements). So can in the specialist circles under the well-known term "ice plate ride", after a slide abruptly there is frictional engagement again, the peak torque loads are so great that for Maintenance or even a necessary increase in the contact pressure on the friction drive the specific Provision of pressure oil at least (in terms of quantity) meets the adjustment volume supply needs must speak. Even on the basis of such aspects, it is always sufficient for all cases present pressure medium supply, which does not drop under load, as is the case with displacement pumps offer assets, current.

When it comes to the supply of pressure, lubricants and coolants for automatic gearboxes, the pressure is similarly stored oil supply problems. There is a particular requirement that within extremely short periods of time locking operations must be effected on hydraulic clutches, which requires a quantity-specific high pressure medium supply. An obvious use of However, pressure storage is to be avoided for such spontaneous "supply surges", especially because of the over spiraling own inertia of the pressure medium, which the usable pressure potential of the memory diminishes, not suitable. Positive displacement pumps, which have a correspondingly large size, have proven effective Delivery volume sufficient pressure medium supply for the short clutch closing processes inevitably always (due to the form-locking principle of funding) always ensure. Between the sporadically occurring switching operations, this also promotes under the operating pressure Pump practically useless and therefore lossy.

The aim and intention of the present inventive concept is to create a low-loss, constructive low-cost pressure medium supply for both applications.

The solution lies in the partial recovery of those contained in such hydraulic circuits mechanical energy used on the he stated in the claims and the description way according to the invention. The main characteristic is that excess print medium, or something that already does work but still has pressure to relax has, preferably in connection with the performance of lubrication and cooling tasks in particular for the active friction parts of the friction drive in CVT's in a targeted jet with largely tangential impact angle on an impact or deflection surface of a rotating or translating Gear base - advantageously the tension or push link belt - is fed so that action forces of the oil jet exert a force or torque impulse on this transmission section and thus part of the excess hydraulic energy again as mechanical energy Drive path benefits.

Advantages of individual design features are among the exemplary embodiment descriptions cited.  

Embodiments

Fig. 1 shows a schematic representation of a CVT with a device according to the invention.

On the input and output shafts 1 and 2 are the conical friction disks 3 and 4 arranged in pairs, between which the transmission line 5 is wedged in a frictionally engaged manner. This can be either a link chain acting as a tension cord or a push link belt. The running circles 6 a, 6 b and 7 a, 7 b illustrate the different geometric relationships in the extreme control positions. The friction partners are pressed by hydraulic cylinders (not shown), which are supplied via lines 8 and 9 . The translation-determining pressure ratio of both Druckzy cylinder is controlled according to a known embodiment by the flow divider 10 designed as a multi-edge control slide, actuated by a proportional magnet 11 , controlled by an electronic on-board control and regulating device 12 . The pressure oil is supplied by pump 13 , which is preferably driven by the input base of the transmission. The excess fluid for the pressure cylinder and intended for lubrication and cooling purposes, in particular the friction partners 3 , 4 and 5, is supplied to the spray nozzle 16 via line 15 . In the present exemplary embodiment, this consists of its housing 17 , which essentially has a tapered, conical inner needle valve seat and a cylindrical inner contour, with a piston 18 displaceable therein, which merges into a valve needle 19 and is acted upon on one side by compression spring 20 . The emerging oil jet, whose (speed) energy content comes from the previous pressure energy, is directed towards the largely tangential impact direction on the transmission line 5 . In a design of this element 5 as a (known PIV) Leschenkette offer gaps between the individual links and in the plate package between the plates themselves enough access to the oil jet to effective baffle and deflection surfaces, for. B. on lots of the cradle pressure pieces, on the end faces of the tabs, and end faces of the clamp tabs. An arrangement of the nozzle 16 on the inside of the tensile cord 6 promises more efficient impact requirements for the jet. B. in the indicated spatial positioning 22nd Special configurations of such oil jet-forming valve elements as described under FIG. 11 promise further advantages.

When using (well-known van Doorne) push link belts is - because of their smooth and dense surface structure - the extension to create impact and deflection surfaces individual links. Because of the limited curvature (compared to the link chain) radius such protruding structures can be arranged inside. This comes from the desire against the beam feed from the inside, since these strands have a dense structure, and from illuminated on the outside, the contact surface lubrication would be insufficient.

Because of the different inlet angles in the case of translation variation, it is advantageous to arrange the nozzle 71 in an articulated manner and to provide only one corresponding adjustment mechanism which adjusts the oil jet direction depending on the translation.

The spray nozzle version 16 shown allows the variation of the "pre-pressure" and thus its adaptation to the respective operating conditions. Compression spring 20 causes a Überdruckventilfunk tion, so that the essential requirement for an always ensured basic pressure is met. According to the requirements, the opening pressure or the operating position of the needle valve and thus the admission pressure in the hydraulic system of the CVT's (in the line system 15 , 14 ) is influenced by pressurizing the spring pressure cylinder chamber. This control pressure is adjusted by the proportional magnet 23 via the electronic control device 12 . Pressure relief valve 24 is a common safety device for limiting the pump pressure, which also limits the overall transmission load.

Fig. 2, 3 and 4 show a device according to the invention, wherein the active oil jet is directed to a gear, in particular for applications in which a constant pressure to be maintained in a hydraulic circuit, wherein the excess fluid is used for lubrication and cooling purposes , e.g. B. in automotive gearboxes.

The axially displaceable pressure piston 31 is located in a nozzle housing 30 and merges into a valve cone 32 . This is acted upon by force from the compression spring 33 , on the one hand, and by the oil pressure of the pretensioning system, on the other hand. The valve needle-side supply line 43 is connected to the bias circuit of a CVT.

For a more ideal deflection of the oil jet, the teeth 36 of a gear 35 (at an inactive edge point) have trough-shaped recesses 37 , preferably also formed as a radius in the base of the tooth. Since in the preferred application, automatic gearshift controls, where it appears necessary to use several such self-regulating spray nozzles, such nozzles could affect each other's function by vibration effects during the closing processes, as well as to ensure a minimum oil supply at each base, a close bypass connection in the jet direction is in the form of the cone valve seat of holes 38 and 39 created. To dampen vibrations on the valve body 31/32 , the spring chamber 40 is designed as a (closed) damping chamber with a throttled outlet 34 . To in turn with spontaneous front-end needs in the "high pressure circuit", e.g. B. when changing the coupling combinations, where valuable the entire flow rate for filling their pressure chambers is required to enable the fastest short-term closing operations on the present valve, a one-way (opening) valve 42 is arranged.

Modified Figs. 5 and 6 known (PIV) link chains.

Items 40 , 42 and 43 are link plates, which are in the Zugver bundle by means of weighing and pressure bolts 41 a and 41 b. Conventionally, the end parts of such link plates have a largely rounded, convex end contour 42 . In order to offer the oil jet attacking and deflecting surface hitting at an acute angle, the link end contours 46 are concave, which can pivot the adjacent link plate contactlessly and force the incoming oil jet to redirect.

Also known are link chain designs, the divisions (joint spacing) and link arrangements and assignments are such that link plates 49 of the next link plate package still protrude between the link plates 47 of the own link plate package. In the case of such link brackets (the graduation scales taken from FIG. 5 in the referring FIG. 6 are not correct for this) there is easily the possibility of a more pronounced and therefore more efficient beam deflection section 50 with the trough-like final contour for reasons of space.

Furthermore, such known tension cord variants have so-called “clip tabs” which are located therein exist that the tab package laterally encompassing tabs with an outside around the package guided bracket are connected. An inventive modification, not shown, of such Clip tabs is that on the side facing the oil jet the upper bracket is crimped in a trough-shaped manner so that a targeted guiding effect to the friction parts or or and acts to flow through the train.

FIGS. 7 to 9 show sections and views of prior art (van Doorne-) push belts with inventively modified pressure pieces.

The thrust pieces consisting essentially of head 55 and wedge part 56 , with the steel bands 57 embedded between them, conventionally have recesses 58 , 59 on their inside. In order to create oil jet, impact and deflection bases, individual pressure pieces 60 , 61 , 62 are designed to be extended towards the inside at certain intervals. These elongated parts 63 can advantageously be additionally curved. Contrary to the illustration, protruding baffles can alternatively also be directed outwards (upwards in the picture). In this case, however, a suitable curvature formation is recommended such that the impinging oil jet is directed to the friction parts, or, respectively, and flushes the pressure pieces laterally. For acoustic reasons, it is necessary to arrange the distributions of these special pressure pieces 60 , 61 , 62 irregularly in the strand.

Fig. 10 shows a modified version of Fig. 1, in which the entire pressure potential of the hydraulic supply device of the CVT is used for the conversion into speed energy, with a novel CVT control strategy. Positions 1 to 9 correspond to those given or described in FIG. 1. The pressure medium supply of the cylinder lines 8 and 9 takes place by pump 65 via a 4/2-way valve 66 , actuated by solenoid 67 , controlled by the electronic control and regulating device 68. Alternatively, a pressure cylinder is connected directly to the pump, and the other with the preload pressure circuit 69 . The pump pressure, and thus the absolute control pressure, is determined by a controllable nozzle valve 71 connected via line 70 . The pressure level of the bias circuit is also regulated by valve 72 with its proportional magnet 82 by the control device 68 . In order to allow the pushed-in fluid to flow out of the pressure cylinders while the required basic pressure remains, there is a valve 74, also controlled by 68, with its actuator 75 , the response threshold of which lies above that of the valve 72 , between the bias circuit and the free atmosphere. The oil jet nozzle valve 71 consists essentially of the needle valve 76/77 , with the pressure and guide piston 79 adjoining the valve cone 77 and the proportional magnet 82 connected via connection 81 , which is also controlled by 68. In order to keep the actuating forces low, the back pressure chamber 80 of the piston 79 is acted upon as a partial compensation for the control pressure acting in the pressure chamber 78 with a preload pressure level. Pressure relief valve 84 limits and secures the hydraulic system against overpressure. In the present illustration, the so-called “control pressure”, which carries out the translation-determining functions, is regulated by means of the jet-forming discharge valve 71 . As an alternative to the present example, the "pre-pressure" on the driven pulley set, which determines the frictional engagement, can of course also be regulated by a corresponding circuit.

Fig. 11 shows a indeed known, but relatively new type CVT control scheme incorporating the device of the invention:
An oil pump 90 supplies the pressure cylinder lines 8 and 9 of a CVT via the lines 91 a and 91 b, the check valves 94 and 95 connected in between, which block the pump 90 . The pump pressure is the "pre-pressure" that determines the frictional engagement. This is determined by an oil jet-forming valve device 100 , which is connected to the pump 90 via the lines 91 c and 93 with an arranged in between, by a torque sensor 98 controlled differential pressure valve 97 . A "control pressure" which effects the transmission adjustment is generated by a second pump 96 which can be operated in both directions of rotation and is arranged between the pressure cylinder lines 8 and 9 . The check valves 94 and 95 prevent pressure level compensation in the cylinder lines. The from an electrical. Control device 110 controlled pump 96 economically brings only the currently required adjustment volume to valve device 100 consists of the actual needle valve 101/102 , with a subsequent hydraulic piston 103 and an associated actuator 106 , and can be adjusted in various ways:

• 1) by actuator 106 alone;
• 2) by the pressure valve 97 controlled by a torque sensor 96 which is known in the industry and which supplies a control pressure proportional to the required “pre-pressure” via line 93 , the active surfaces of the piston 103 on both sides being matched in such a way that the pre-pressure which is set is slightly above the nozzle control pressure level. Volume and pressure losses in the control valve 97 are thus small, the conversion of the pressure energy into speed energy takes place largely in the jet-forming nozzle 100, which acts as a “pre-load valve”.

Most of the energy contained in the pretensioning circuit is therefore available for regenerative use. Alternatively or additionally, the control element 99 can be used by the electronic control device 110 to intervene, which is useful and predetermined for special operating states and certain functional sequences.

Since, according to the known laws of hydromechanics, the efficiency of the transfer of energy contents of a liquid jet to a baffle or deflection plate is greatest when its absolute speed of movement is about half the speed of the absolute jet occurrence, another is used to adapt and optimize these conditions Proposed device, not illustrated, suggested:
According to the practical, usually existing conditions at the CVT, it can be expected that the jet speed resulting from the usual operating pressures will be above the peripheral speed of the tension or push belt. For this purpose, the inclusion of an injector device is proposed, which enriches the emerging oil jet from an oil supply or increases its quantity. The speed energy of the incoming pressure oil is reduced by using this energy as acceleration energy for the added oil mass. In the subsequent impact of the mass-enlarged beam, this energy portion - of course reduced by unavoidable implementation losses of the previous "enrichment process" - is boosted by the impulse force.

A major advantage in all of the present exemplary embodiments is that the oil jet-forming nozzles are equally mandatory elements of the hydraulic control of the CVT, and it also has an advantageous effect that when the force impulse of the oil jet is introduced onto the tension or push link belt 5 arranged in the drive train, the mandatory requirement intensive oiling and cooling of the friction parts of the friction drive is done or connected at the same time. The construction effort for the required elements is thus minimal.

bibliography
1) Dr.-Ing. O. Dittrich "The continuously variable chain transmission as the main drive in a motor vehicle" VDI reports 803 ;
2) Prof. Dr.-Ing. R. Höhn: "Why stepless transmissions in vehicles" VDI reports 803 ;
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4) Dipl.-Ing. P. Heidemayer: "Why stepless transmissions in cars?" Sem. No. 811120021 Technical Academy Wuppertal;
5) Dr.-Ing. H. Röper: "Status of CVT development - advantages and limitations of the system" 2 . Aachen Colloquium: Vehicle and Engine Technology 89 ;
6) Dipl.-Ing. U. Eggert: "CVT - Electronic Control and Driving Dynamics" VD1 - Reports 803 ;
7) H. Röper: "Requirements for the pressure oil supply of hydraulically controlled CVT transmissions" antriebstechnik 26 (1987) No. 8;
8) W. Schopf "Continuously adjustable belt transmission" published application DE 42 22 636 A1;
9) W. Schopf "Drive for a pressure medium pump in a drive arrangement formed by the drive motor and a transmission-adjustable transmission" Patent DE 39 00 062 C2;
10) W. Schopf "multi-circuit control pump" published application DE 39 13 414 A1;
11) W. Schopf "Pump combination with volume control device" Patent DE 32 10 759 C2;
12) W. Schopf: "Adaptive electronic contact pressure control for bevel friction disc belt transmission especially for motor vehicles (CVT)" Patent specification DE P 43 12 745;
13) G. Bornmann: "Device for translation control of a continuously variable conical pulley belt transmission for motor vehicles" Patent DE 39 34 506 C1.

Claims (24)

1. Device on mechanical gearboxes for recovering mechanical, unused energy from pressure oil systems on CVT's in the form of conical pulley belt drives with hydraulic devices consisting essentially of a hydraulic pump, hydraulic devices for applying and controlling the frictional contact pressure of the friction drive and its translation adjustment, as well as Lubrication and cooling, in particular of the active friction parts of the friction drive, characterized in that at least one outlet of a pressure, lubricant or coolant circuit ( 14 ) takes place via a pressure-reducing, oil jet-forming valve device ( 16 , 30 , 71 , 100 ), the oil jet escaping largely tangential direction of incidence is directed to a rotating or translating part ( 5 , 37 ) of the transmission, which is suitable or is designed such that the beam is at least braked by this incidence base, striving for deflection t, so that action forces of the jet impart a force or torque impulse to this transmission part, the valve device ( 16 , 30 , 100 ) being of such a type and incorporated into the transmission hydraulic system that the pressure potential of this hydraulic circuit is largely only in this oil jet-forming valve device ( 16 ; 30 ; 71 ; 100 ) is dismantled. 2. Device on mechanical gearboxes for the recovery of mechanical, unused energy from pressure oil systems of automatic gearshift systems, consisting essentially of several planetary stages that can be switched and combined in the power flow, an associated hydraulic pump, a large number of hydraulic valves for controlling the pressure medium acting on the clutches activating the planetary stages and for Supply of lubricating and cooling oil circuits, characterized in that the outflow of the pressure oil circuit takes place via a pressure-reducing, oil jet-forming valve device ( 30 ), the emerging oil jet is directed in a largely tangential direction of occurrence onto a rotating part ( 35 , 36 , 37 ) of the transmission, which is suitable or is designed so that the jet is at least braked by this tread base, deflected in a striving manner, so that action forces of this jet give this transmission part a torque pulse, the valve device Seal ( 30 ) is so designed and arranged that the pressure potential of this hydraulic circuit is largely reduced only in it. 3. Device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claim 1, characterized in that the oil jet-forming valve device ( 16 , 30 , 71 , 100 ) a known CVT control system, consisting largely of an oil pump ( 13 ), a flow divider ( 10 ), which connects the pressure cylinder lines ( 8 , 9 ) alternatively or throttled metering to the pump ( 13 ) or a "preload circuit" ( 14 ) which determines the frictional connection. 4. Device on mechanical gearboxes for the recovery of unused mechanical energy from pressure oil systems according to claim 1, characterized in that the oil jet forming valve device ( 16 , 30 , 71 , 100 ) is assigned to a CVT hydraulic control device according to FIG. 10, which essentially consists of an oil pump ( 65 ), a changeover valve ( 66 ) which alternatively connects the pressure cylinder lines ( 8 , 9 ) to the pump or a preload pressure circuit ( 69 ), the pump pressure level causing the transmission ratio control from this oil jet-forming valve device ( 71 ) itself and the pressure difference between the control and Admission pressure is determined by a further regulated valve ( 72 ). 5. A device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claim 1, characterized in that the oil jet-forming valve device ( 71 ) is integrated in a CVT hydraulic control system according to FIG. 11 consisting essentially of a first hydraulic pump ( 90 ) with their branched outputs ( 91 a, b, c) leading to the pressure cylinder lines ( 8 , 9 ) and a pressure control valve ( 97 ), and between the pump lines ( 8 , 9 ) there is a connection ( 92 ) in which a second, in both Control pump ( 96 ) which can be operated in the conveying directions and which supplies the adjustment volume of the CVT and doses the control pressure, is also arranged in the cylinder lines ( 8 , 9 ) to the first pump ( 90 ) and check valves ( 94 , 95 ) are arranged, the oil jet-forming valve device ( 100 ) not only with other auxiliary devices, the CVT's pre-pressure level is determined. 6. Device on mechanical gearboxes for recovering mechanical energy from pressure oil systems according to claim 1 and 3 to 5, characterized in that the oil jet from the oil jet-forming controllable valve device ( 16 , 71 , 100 ) largely tangential to the transmission line of the CVT (train or Push link belt) is directed. 7. Device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claim 1 and 3 to 6, characterized in that the oil jet-forming valve device ( 16 , 71 , 100 ) is movably arranged in such a way that the oil jet gear ratio depending on the respective position the transmission line ( 5 ) is tracked. 8. Device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claims 1 and 3 to 7, characterized in that the positioning and arrangement of the jet-forming controllable valve device ( 16 , 71 , 100 ) is such that the point of impact of the oil jet on the transmission line is in its lead-in area of the disc wedge. 9. A device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claim 2, characterized in that the oil jet of the oil jet-forming valve device ( 30 ) is directed to a gear ( 35 ), or another rotating gear component suitable as a jet impact surface. 10. Device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claims 2 and 9, characterized in that the illuminated gear ( 35 ) preferably has trough-like recesses ( 37 ) laterally outside of its load-bearing tooth flank section on the tooth flanks. 11. Device on mechanical gearboxes for recovering mechanical energy from pressure oil systems according to claim 1 and 3 to 8, characterized in that the transmission line ( 5 ) consists of conventional known CVT transmission line designs, but has modifications in a way that for better beam impact or deflection appropriate contours ( 44 , 45 , 46 , 60 , 63 ) are incorporated or arranged. 12. A device on mechanical gearboxes for the recovery of unused mechanical energy from pressure oil systems according to claim 1, 3 to 8, 10 and 11, characterized in that the tabs ( 40 , 47 , 49 ) of tension cords (PIV system) at their ends or in have trough-like recesses ( 45 , 51 ) in the middle, firstly the conventionally rounded endings being convex (50, 56) and web-like configurations ( 44 , 45 ). 13. A device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claim 1, 3 to 8, 10 and 11, characterized in that the tabs ( 40 , 47 , 49 ) of tension cords (system PIV) with their convex ends ( 50 ) protrude into the spaces between tabs ( 47 ) of adjacent tab packs. 14. Installation on mechanical gearboxes for the recovery of unused mechanical energy from pressure oil systems according to claim 1, 3 to 8, 10 and 11, characterized in that on tension cords (PIV system) "clip tabs" at the top of those enclosing the pool packages In a suitable manner, connecting pieces unfolded portions serve as Impact and guide surface for the oil jet. 15. Device on mechanical gearboxes for the recovery of unused mechanical energy from pressure oil systems according to claim 1, 3 to 8, 10 and 11, characterized in that individual pressure pieces ( 55/56 ) of thrust link belts (System van Dorne) against the otherwise usual lower recesses ( 58 , 59 ) have extensions ( 61 , 63 ). 16. Device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claim 1, 3 to 8, 10 and 11, characterized in that individual pressure pieces ( 55/56 ) of thrust link belts (System van Doorne) over that of the other pressure pieces ( 55 / 56 ) have protruding extensions ( 61 , 63 ) which are additionally curved ( 63 ) to accommodate oil jet deflection. 17. Installation on mechanical gearboxes for the recovery of unused mechanical energy from pressure oil systems according to claim 1 and any other above claims, thereby characterized in that on tension cords and push link belts for the purpose of beam impact and conductivity attached devices are distributed unevenly over the strand length. 18. Device on mechanical gearboxes for the recovery of unused mechanical energy from pressure oil systems according to claim 1 and 2 and any other preceding claims, characterized in that the jet-forming valve device ( 16 , 30/32 and 71 ) with at least one needle nozzle ( 17/19 ) a pressure cylinder ( 18 , 31 , 79 ) with two pressure spaces acting on both sides. 19. Device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claim 1 and 2 and any other preceding claims, characterized in that the jet-forming valve device ( 16 , 30 , 71 , 100 ) with an externally controllable actuator ( 21 , 82 , 106 ) is equipped, preferably consisting of a proportional magnet. 20. Device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claim 2, characterized in that several jet-forming valve devices ( 16 , 30 , 71 ) are used in parallel in supply circuits with a largely constant pressure level. 21. Device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to any preceding claims, characterized in that the oil pressure-forming valve device ( 16 , 71 , 100 ) determining the preload pressure according to those described in the published patent application DE P 43 12 745.2, or in claim taken control functions are controlled. 22. Installation on mechanical gearboxes for the recovery of unused mechanical energy from pressure oil systems according to claim 1 and 2 and further preceding claims, characterized characterized in that the oil jet-forming discharge nozzle has an injector device with a connecting line to one Oil reservoir; with a functional behavior such that the oil flow coming from the pressure oil circuit by means of the injector effect, fluid is sucked out of the reservoir and the emerging oil jet is added. 23. Installation on mechanical gearboxes for the recovery of unused mechanical energy from pressure oil systems according to claim 1, 2 and 22, characterized in that the jet-forming outlet-injector combination can thus be controlled according to a predetermined mode is that the proportion of the admixable fluid, and thus also the jet exit speed, is regulated becomes. 24. Device on mechanical gearboxes for recovering unused mechanical energy from pressure oil systems according to claim 1 and 5, characterized in that the jet-forming outlet valve ( 100 ) has a pressure piston ( 103 ) acted on on both sides, the effective piston surfaces of which are matched so that for positioning the valve body ( 102 ) and thus only a small pressure difference of the total available or to be reduced pressure level ( 91 a, b, c,) for regulating the dynamic pressure is brought about by a preferably externally assigned, controllable differential pressure valve ( 97 ), the control or differential pressure ( 91 c - 93 ) does not exceed 15% of the total prevailing pressure potential ( 91 a, b, c).